JPWO2018116413A1 - Distributor, heat exchanger, and refrigeration cycle device - Google Patents

Abstract

The distributor according to the present invention communicates the fluid inlet, the plurality of fluid outlets, the fluid inlet and the plurality of fluid outlets, and distributes the fluid flowing in from the fluid inlet to the plurality of fluid outlets. And a plurality of heat transfer tube insertion portions formed in the respective facing directions of the plurality of fluid outlet portions and into which the heat transfer tubes are inserted, and the plurality of heat transfer tube insertions are respectively inserted into the plurality of fluid outlet portions. The tip of the heat transfer tube inserted into the part is connected.

Description

  The present invention relates to a distributor, a heat exchanger, and a refrigeration cycle apparatus used for a heat circuit or the like.

The heat exchanger has a flow path (pass) in which a plurality of heat transfer pipes are arranged in parallel in order to reduce pressure loss of the refrigerant flowing in the heat transfer pipe. At the refrigerant inlet of each heat transfer tube, for example, a header or a distributor, which is a distributor that evenly distributes the refrigerant to each heat transfer tube, is disposed.
Equal distribution of the refrigerant to the plurality of heat transfer tubes is important in securing the heat transfer performance of the heat exchanger.

As such a distributor, for example, by laminating a plurality of plate-like members, a distribution flow channel which branches into a plurality of outlet flow channels with respect to one inlet flow channel is formed, and each of the heat exchangers It has been proposed that a refrigerant is distributed and supplied to a heat pipe (see, for example, Patent Document 1).
The distributor described in Patent Document 1 is configured by alternately laminating a bear material, which is a plate-shaped body to which a brazing material is not applied, and a clad material, which is a plate-shaped body to which a brazing material is applied, The end of the heat transfer tube is inserted at the outermost side of the.

WO 2015/004719

  In the distributor described in Patent Document 1, the branch flow path formed in the distributor and the space into which the heat transfer tube is inserted are separately provided. That is, in the distributor described in Patent Document 1, a plate-like body for forming a space into which the heat transfer tube is inserted has been required. The increase of the plate-like body leads to the enlargement of the distributor. On the other hand, further miniaturization is required of distributors, including distributors that are not laminates of plate-like bodies, and there is room to pursue miniaturization.

  The present invention has been made on the background of the above-described problems, and an object of the present invention is to provide a distributor, a heat exchanger, and a refrigeration cycle apparatus in which the miniaturization is pursued.

  The distributor according to the present invention communicates the fluid inlet, the plurality of fluid outlets, the fluid inlet and the plurality of fluid outlets, and allows the fluid flowing from the fluid inlet to be the plurality of fluid outlets. And a plurality of heat transfer tube insertion portions formed in the respective facing directions of the plurality of fluid outlet portions and into which the heat transfer tubes are inserted, and each of the plurality of fluid outlet portions A tip end portion of the heat transfer tube inserted into the plurality of heat transfer tube insertion portions is connected.

A heat exchanger according to the present invention comprises the above-mentioned distributor, and a plurality of heat transfer pipes into which the fluid flowing out from the plurality of fluid outlet portions of the distributor flows.
A refrigeration cycle apparatus according to the present invention includes the above-described heat exchanger as at least one of an evaporator and a condenser.

In the distributor according to the present invention, since the tip of the heat transfer tube is connected at the fluid outlet, the length in the fluid flow direction can be shortened, and miniaturization can be realized.
Since the heat exchanger according to the present invention includes the above-described distributor, at least the miniaturization thereof is realized.
Since the refrigeration cycle apparatus according to the present invention includes the above-described heat exchanger, at least the miniaturization thereof is realized.

It is a figure which shows roughly the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view in the state which disassembled the dispenser which concerns on Embodiment 1 of this invention. It is the perspective view which expanded A part shown in FIG. It is the figure which expanded the A section shown in FIG. 2, and was seen from the flow-path inlet side. It is an expanded view of a distributor concerning Embodiment 1 of the present invention. It is a longitudinal cross-sectional view of the distributor which concerns on Embodiment 1 of this invention. It is a figure explaining the flow of the manufacturing method of the heat exchanger concerning Embodiment 1 of the present invention. It is a longitudinal cross-sectional view which shows the flow of the refrigerant | coolant of the distributor completed by the manufacturing method of FIG. It is the schematic for demonstrating the modification 1 of the heat exchanger which concerns on Embodiment 1 of this invention. It is the schematic for demonstrating the modification 2 of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view in the state which disassembled the dispenser which concerns on Embodiment 2 of this invention. It is the figure which expanded B part shown in FIG. 11 and was seen from the flow-path inlet side. It is the schematic which expanded and showed the connection part of the heat exchanger tube of the distributor which concerns on Embodiment 2 of this invention. It is an expanded view of the splitter which concerns on Embodiment 2 of this invention. It is a longitudinal cross-sectional view of the distributor which concerns on Embodiment 2 of this invention. It is a circuit block diagram which shows roughly an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 3 of this invention.

Hereinafter, a distributor, a heat exchanger, and a refrigeration cycle apparatus according to the present invention will be described using the drawings.
The configurations, operations, and the like described below are merely examples, and the distributor, the heat exchanger, and the refrigeration cycle apparatus according to the present invention are not limited to such configurations, operations, and the like. Further, in the respective drawings, the same or similar components are denoted by the same reference symbols, or the reference symbols are omitted. Moreover, the illustration of the fine structure is simplified or omitted as appropriate. In addition, redundant or similar descriptions are appropriately simplified or omitted.

  Moreover, although the case where the distributor and heat exchanger which concern on this invention are applied to the air conditioning apparatus which is an example of a refrigerating cycle apparatus is demonstrated below, it is not limited to such a case, For example, The present invention may be applied to other refrigeration cycle devices having a refrigerant circulation circuit. Moreover, although the case where a refrigerating cycle apparatus is what switches heating operation (heating operation) and cooling operation (cooling operation) is demonstrated, it is not limited to such a case, Only heating operation or cooling operation It may be done.

Embodiment 1
A distributor and a heat exchanger according to Embodiment 1 of the present invention will be described.
<Configuration of Heat Exchanger 1>
The schematic configuration of the heat exchanger 1 according to the first embodiment will be described below.
FIG. 1 is a diagram schematically showing the configuration of the heat exchanger 1 according to the first embodiment. In addition, in FIG. 1 or less, the flow direction of a refrigerant | coolant is shown by the black arrow.

  The heat exchanger 1 includes a first distributor 2, a second distributor 3, a plurality of heat transfer pipes 4, and a plurality of fins 5. The second distributor 3 may use the same type of distributor as the first distributor 2 or may use a different type of distributor than the first distributor 2.

At least one distribution channel 2 a is formed inside the first distributor 2. A refrigerant pipe is connected to the inflow side of the distribution flow path 2a. A plurality of heat transfer pipes 4 are connected to the outflow side of the distribution flow path 2a.
The first distributor 2 corresponds to the “divider” of the present invention.
A merging channel 3 a is formed in the second distributor 3. A plurality of heat transfer pipes 4 are connected to the inflow side of the merging flow path 3a. A refrigerant pipe is connected to the outflow side of the merging flow path 3a.

The heat transfer tube 4 is a flat tube or a circular tube in which a plurality of flow paths are formed. The heat transfer tube 4 is made of, for example, aluminum. A plurality of fins 5 are joined to the heat transfer tube 4.
The fins 5 are made of, for example, aluminum. The heat transfer tubes 4 and the fins 5 are joined, for example, by brazing. Although FIG. 1 shows the case where the number of heat transfer tubes 4 is four, it is not limited to such a case. Moreover, in Embodiment 1, the case where the heat transfer tube 4 is a flat tube shall be demonstrated to an example.

<Flow of refrigerant in heat exchanger>
The flow of the refrigerant in the heat exchanger 1 will be described below.
The refrigerant flowing through the refrigerant pipe flows into the first distributor 2, is distributed by the distribution flow path 2 a, and flows out to the plurality of heat transfer pipes 4. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of heat transfer pipes 4. The refrigerant flowing through the plurality of heat transfer pipes 4 flows into the joining flow path 3a of the second distributor 3 to join and flow out to the refrigerant pipe. In the heat exchanger 1, the refrigerant can flow backward, that is, can flow from the second distributor 3 toward the first distributor 2.

<Configuration of First Distributor 2>
The configuration of the first distributor 2 will be described below. First, the case where the first distributor 2 is a laminated header will be described as an example.
FIG. 2 is a perspective view of the first distributor 2 in a disassembled state. FIG. 3 is an enlarged perspective view of a portion A shown in FIG. FIG. 4 is an enlarged view of a portion A shown in FIG. 2 as viewed from the channel inlet side. Note that FIG. 4 also illustrates the heat transfer tube 4.

  As shown in FIG. 2, the first distributor 2 has a plate-like body 11. The plate-like body 11 is formed by alternately laminating a first plate-like member 12_1 to a first plate-like member 12_4 to be a bear material and a second plate-like member 13_1 to a second plate-like member 13_3 to be a clad material. It is formed. The first plate member 12_1 and the first plate member 12_4 are stacked on the outermost side in the stacking direction of the plate members 11. Hereinafter, the first plate-like member 12_1 to the first plate-like member 12_4 may be collectively referred to as a first plate-like member 12. Similarly, the second plate member 13_1 to the second plate member 13_3 may be collectively referred to as a second plate member 13.

The first plate member 12 is made of, for example, aluminum. The brazing material is not applied to the first plate-like member 12. In each of the first plate-like members 12, through holes 12a_1 to 12a_4 to be the distribution flow path 2a are formed. The through holes 12a_1 to 12a_4 penetrate the front and back of the first plate-like member 12. When the first plate member 12 and the second plate member 13 are stacked, the through holes 12a_1 to 12a_3 function as a part of the distribution flow path 2a.
The through holes 12a_1 function as fluid inlets into which a fluid such as a refrigerant flows.
The end of the through hole 12a_3 functions as a fluid outlet from which a fluid such as a refrigerant flows out.
The through hole 12a_4 functions as the heat transfer tube insertion part 2b, so that no fluid such as a refrigerant flows.

The second plate-like member 13 is made of, for example, aluminum, and is formed thinner than the first plate-like member 12. A brazing material is applied to at least the front and back surfaces of the second plate-like member 13. In each of the second plate-like members 13, a through hole 13a_1 and a through hole 13a_2 to be the distribution flow path 2a are formed. The through holes 13a_1 to 13a_3 pass through the front and back of the second plate-like member 13. When the first plate member 12 and the second plate member 13 are stacked, the through holes 13a_1 and the through holes 13a_2 function as part of the distribution flow path 2a.
The through hole 13a_3 functions as the heat transfer tube insertion part 2b, so that no fluid such as a refrigerant flows.

The through hole 12a_1 formed in the first plate member 12_1, the through hole 13a_1 formed in the second plate member 13_1, and the through hole 13a_2 formed in the second plate member 13_2 have a circular flow passage cross section. It is formed through. A refrigerant pipe is connected to the through hole 12a_1 which functions as a fluid inlet. For example, a nozzle or the like may be provided on the surface of the first plate member 12_1 on the refrigerant inflow side, and the refrigerant pipe may be connected via the nozzle or the like, and the inner peripheral surface of the through hole 12a_1 is a refrigerant pipe The refrigerant pipe may be directly connected to the through hole 12a_1 without using a die or the like.
In addition, a flow path cross section is a cross section which cut the flow path in the direction orthogonal to the flow of a fluid.

  The through hole 12a_2 formed in the first plate-like member 12_2 is, for example, formed in a Z-shaped flow passage cross section. The through hole 13a_1 of the second plate member 13_1 stacked on the refrigerant flowing side of the first plate member 12_2 is formed at a position facing the center of the through hole 12a_2. The through hole 13a_2 of the second plate member 13_2 stacked on the refrigerant outflow side of the first plate member 12_2 is formed at a position facing the end of the through hole 12a_2.

  The through hole 12a_3 formed in the first plate-like member 12_3 is, for example, penetratingly formed in a shape in which a flow passage cross-sectional Z-shaped portion and a flow passage cross-sectional linear portion are combined. In addition, in the following, the flow path cross-sectional Z-shaped portion is referred to as a Z-shaped portion 112A, and the flow path cross-sectional linear portion is referred to as a linear portion 112B.

  The linear portion 112B communicates with both ends of the Z-shaped portion 112A. That is, the linear portion 112B is formed as a space located at the end of the through hole 12a_3, that is, the end of the distribution flow channel 2a, and corresponds to a portion functioning as a fluid outlet.

  In addition, the lower end of the Z-shaped portion 112A on the upper side of the drawing of the Z-shaped portion 112A communicates with the lower side of the linear portion 112B located on the upper side of the drawing in FIG. Further, the lower end of the Z-shaped portion 112A in the drawing surface is in communication with the upper side of the linear portion 112B located on the lower side in the drawing in FIG. The two straight portions 112B are parallel to one another. Furthermore, as shown in FIG. 4, the opening area of the linear portion 112 </ b> B is larger than the opening area of the distal end portion 4 a of the heat transfer tube 4.

  The through hole 13a_2 of the second plate member 13_2 stacked on the side where the refrigerant of the first plate member 12_3 flows in is formed at a position facing the center of the through hole 12a_3. The through hole 13a_3 of the second plate member 13_3 stacked on the opposite side to the second plate member 13_2 of the first plate member 12_3 is formed at a position facing the linear portion 112B of the through hole 12a_3.

When the first plate member 12 and the second plate member 13 are stacked, a through hole formed in the first plate member 12 and a through hole formed in the second plate member 13; Communicate with each other to form the distribution flow channel 2a. That is, when the first plate-like member 12 and the second plate-like member 13 are laminated, the adjacent through holes communicate with each other, and the first plate-like member 12 or the first plate-like member 12 It is closed by the two plate-like members 13, and the distribution flow path 2a is formed.
In the first distributor 2, the distribution flow channel 2a is illustrated as having four fluid outlets for one fluid inlet, but the number of branches is limited to four. It is not something to do.

  As shown in FIG. 2, the through hole 12a_4 formed in the first plate member 12_4 and the through hole 13a_3 formed in the second plate member 13_3 are linear portions 112B which are the end portions of the through holes 12a_3. The heat transfer tube 4 functions as a heat transfer tube insertion part 2 b which is formed in the facing direction of the heat transfer tube 4 and into which the end 4 a of the heat transfer tube 4 is inserted. That is, the through holes 12a_4 and the through holes 13a_3 are formed at positions facing the linear portion 112B located on the extension of the heat transfer tube 4, and the heat transfer tube 4 is inserted into this position. The heat transfer tube 4 is connected to the first distributor 2.

Further, the tip end portion 4a of the heat transfer tube 4 may be at the position of the through hole 13a_3 of the second plate member 13_3, or even at the position of the linear portion 112B of the through hole 12a_3 of the first plate member 12_3. Good. That is, the tip end 4a of the heat transfer tube 4 may be at a position not in contact with the second plate member 13_2.
The inner peripheral surface of the through hole 12a_4 of the first plate member 12_4 is fitted to the outer peripheral surface of the heat transfer tube 4. The fitting should have a gap that allows the heated brazing material to penetrate by capillary action.

<Flow of refrigerant in first distributor 2>
The flow of the refrigerant in the first distributor 2 will be described below.
FIG. 5 is a development view of the first distributor 2. FIG. 6 is a longitudinal sectional view of the first distributor 2. In FIG. 6, for convenience of explanation, the thickness of the plate-like body is schematically illustrated as being uniform. Further, FIG. 6 shows a cross section cut along the fluid flow direction.

  As shown in FIGS. 5 and 6, the refrigerant flowing through the refrigerant pipe flows into the inside of the first distributor 2 with the through hole 12a_1 of the first plate member 12_1 as a fluid inlet. The refrigerant flowing from the through hole 12a_1 flows into the through hole 13a_1 of the second plate member 13_1.

  The refrigerant flowing from the through hole 12a_1 of the first plate member 12_1 into the through hole 13a_1 of the second plate member 13_1 flows into the center of the through hole 12a_2 of the first plate member 12_2. The refrigerant that has flowed into the center of the through hole 12a_2 of the first plate member 12_2 strikes the surface of the second plate member 13_2 stacked adjacent to it and branches off, and the end of the through hole 12a_2 of the first plate member 12_2 Flow. The refrigerant reaching the end of the through hole 12a_2 of the first plate member 12_2 passes through the through hole 13a_2 of the second plate member 13_2 and flows into the center of the through hole 12a_3 of the first plate member 12_3.

  The refrigerant that has flowed into the center of the through hole 12a_3 of the first plate member 12_3 strikes the surface of the second plate member 13_3 stacked adjacent to it and branches off, and the end of the through hole 12a_3 of the first plate member 12_3. Flow. The linear portion 112B which is the end of the through hole 12a_3 of the first plate member 12_3 functions as a fluid outlet, and the refrigerant reaching the end of the through hole 12a_3 of the first plate member 12_3 is a through hole 13a_3 or flows into the inside of the heat transfer tube 4 from the tip 4a of the heat transfer tube 4 located in the through hole 12a_3.

  The refrigerant that has flowed into the heat transfer tube 4 passes through the area located inside the through hole 13a_3 of the second plate member 13_3 and the inside of the through hole 12a_4 of the first plate member 12_4, and the fins 5 of the heat transfer tube 4 It flows into the joined area.

Next, the case where the first distributor 2 is an integral header will be described as an example.
FIG. 7 is a diagram for explaining the flow of the method of manufacturing the heat exchanger 1. First, a method of manufacturing the first distributor 2 using the lost wax method will be described.

  First, in step 0, a mold to be the distribution channel 2a of the first distributor 2 is manufactured. In step 1, wax is poured into the mold produced in step 0 to produce a wax mold (wax pattern 2a_1) having the same shape as the distribution flow path 2a. In step 2, the wax pattern 2a_1 is fixed to the mold 2_1 to be the first distributor 2, and melted aluminum is poured.

Then, in step 3, the hardened aluminum is heated, the wax pattern 2a_1 fixed inside the aluminum is melted and poured out. Thus, the first distributor 2 in which the distribution flow channel 2a is formed is manufactured. Steps 0 to 3 complete the first distributor 2.
Thereafter, in step 4, the heat transfer pipe 4 is connected to the first distributor 2, and other assembly and processing are performed to complete the heat exchanger 1.

  The first distributor 2 manufactured by the lost wax method is different from the first distributor 2 configured as a laminated type header shown in FIG. 2 in that the first distributor 2 does not have the plate-like body 11. However, each function of the first distributor 2 manufactured by the lost wax method is the same as that of the first distributor 2 configured as a laminated header.

<Flow of refrigerant in first distributor 2>
The flow of the refrigerant in the first distributor 2 will be described below. FIG. 8 is a longitudinal sectional view showing the flow of the refrigerant in the distributor completed by the manufacturing method of FIG. In FIG. 8, components or parts corresponding to the components or parts of the first distributor 2 shown in FIG. 2 are illustrated using the same reference numerals. Moreover, in FIG. 8, the correspondence with the plate-like body of the 1st distributor 2 shown in FIG. 2 is shown using the broken line. Moreover, in FIG. 8, for convenience of explanation, the thickness of the plate-like body is illustrated as being substantially uniform. Further, FIG. 8 shows a cross section cut along the fluid flow direction.

The basic refrigerant flow is the same as the refrigerant flow of the first distributor 2 configured as the laminated header described in FIGS. 5 and 6.
The refrigerant having flowed through the refrigerant pipe flows into the inside of the first distributor 2 with the through hole 12a_1 of the first distributor 2 as a fluid inlet. The refrigerant flowing from the through hole 12a_1 flows through the through hole 13a_1 and flows into the center of the through hole 12a_2. The refrigerant flowing into the center of the through hole 12a_2 branches and flows to the end of the through hole 12a_2. The refrigerant reaching the end of the through hole 12a_2 passes through the through hole 13a_2 and flows into the center of the through hole 12a_3.

  The refrigerant flowing into the center of the through hole 12a_3 branches and flows to the end of the through hole 12a_3. The linear portion 112B which is the end of the through hole 12a_3 functions as a fluid outlet, and the refrigerant reaching the end of the through hole 12a_3 is the tip of the heat transfer tube 4 located in the through hole 13a_3 or the through hole 12a_3. It flows into the inside of the heat transfer tube 4 from the portion 4 a.

  The refrigerant that has flowed into the heat transfer tube 4 passes through the inside of the through hole 13a_3 and the region located inside the through hole 12a_4, and flows into the region to which the fins 5 of the heat transfer tube 4 are joined.

<Functions and effects of first distributor 2 and heat exchanger 1>
As described above, in the first distributor 2, by providing the end of the distribution flow channel 2a as the linear portion 112B, it is possible to shorten the length in the flow direction of the refrigerant. For example, in the first distributor 2 shown in FIG. 2, the number of plate members can be reduced, and the thickness of the plate member stacking method can be reduced. Further, in the first distributor 2 shown in FIG. 8, the length in the flow direction of the refrigerant can be made substantially the same as that of the first distributor 2 shown in FIG. 2. Therefore, according to the first distributor 2, cost can be reduced, and miniaturization and weight reduction can be realized.

  Further, since the heat exchanger 1 includes the first distributor 2, the cost required for manufacturing the first distributor 2 and the heat exchanger 1 can be reduced, and downsizing and weight reduction can be realized.

<Modification>
FIG. 9 is a schematic view for explaining a modification 1 of the heat exchanger 1.
In FIG. 2 etc., although the case where the heat exchanger tube 4 was a flat tube was mentioned as the example and demonstrated, as shown in FIG. 9, the heat exchanger tube 4 may be a circular tube. That is, the opening area of the linear portion 112B may be formed larger than the opening area of the tip portion of the heat transfer tube 4 which is an annular ring.

FIG. 10 is a schematic view for explaining a modification 2 of the heat exchanger 1. As shown in FIG.
In FIG. 2 etc., the case where the Z-shaped part 112A communicates at the center in the longitudinal direction of the linear part 112B is described as an example, but as shown in FIG. 10, the Z-shaped part 112A is linear The communication may be performed at a portion other than the longitudinal center of the portion 112B.

Second Embodiment
A distributor according to Embodiment 2 of the present invention will be described.
In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as the first embodiment will be assigned the same reference numerals and descriptions thereof will be omitted.
The heat exchanger provided with the distributor according to the second embodiment is the same as the heat exchanger 1 described in the first embodiment, so the description will be omitted. Further, the distributor according to the second embodiment is referred to as a first distributor 2A.

<Configuration of Distributor According to Second Embodiment>
The configuration of the first distributor 2A will be described below. Here, the case where the first distributor 2A is a laminated header will be described as an example. However, the first distributor 2A may be an integral header, and in this case, the first distributor 2A may be manufactured with reference to FIG. 7.
FIG. 11 is a perspective view in which the first distributor 2A is disassembled. FIG. 12 is an enlarged view of a portion B shown in FIG. 11 as viewed from the channel inlet side. FIG. 13 is a schematic view showing an enlarged connection portion of the heat transfer tube 4 of the first distributor 2A. Note that FIG. 12 also illustrates the heat transfer tube 4. Further, FIG. 13 illustrates a state in which the cross section XX in FIG. 12 is viewed from the upper side of the drawing.

  As shown in FIG. 11, the first distributor 2A has a plate-like body 11. The plate-like body 11 includes a first plate-like member 12_1 to a first plate-like member 12_4 to be a bear, a second plate-like member 13_1 to a second plate-like member 13_3 to be a clad, and a third to be a bear The plate-like member 14 and the fourth plate-like member 15 to be a clad material are laminated and formed. The first plate member 12_1 and the first plate member 12_4 are stacked on the outermost side in the stacking direction of the plate members 11. Hereinafter, the first plate-like member 12_1 to the first plate-like member 12_4 may be collectively referred to as a first plate-like member 12. Similarly, the second plate member 13_1 to the second plate member 13_3 may be collectively referred to as a second plate member 13.

  The first plate member 12 and the second plate member 13 are as described in the first embodiment.

The third plate-like member 14 is made of, for example, aluminum, and the brazing material is not applied like the first plate-like member 12. The third plate member 14 is formed with a through hole 14a_1 and a through hole 14a_2 which are to be the distribution flow path 2a. The through holes 14a_1 and the through holes 14a_2 pass through the front and back of the third plate-like member 14. When the first plate member 12 to the fourth plate member 15 are stacked, the through holes 14a_1 and the through holes 14a_2 function as part of the distribution flow path 2a.
The through hole 14a_2 functions as a fluid outlet from which a fluid such as a refrigerant flows. That is, the through hole 14a_2 is a space located at the end of the distribution flow channel 2a, and corresponds to a portion functioning as a fluid outlet.

  The fourth plate-like member 15 is made of, for example, aluminum, and similarly to the second plate-like member 13, is thinner than the first plate-like member 12. A brazing material is applied to at least the front and back surfaces of the fourth plate member 15. In the fourth plate-like member 15, a through hole 15a_1 and a through hole 15a_2 to be the distribution flow channel 2a are formed. The through holes 15a_1 and the through holes 15a_2 penetrate the front and back surfaces of the fourth plate member 15. When the first to fourth plate members 12 to 15 are stacked, the through holes 15a_1 and the through holes 15a_2 function as part of the distribution flow path 2a.

  The through hole 14a_1 formed in the third plate member 14 and the through hole 15a_1 formed in the fourth plate member 15 are similar to the through hole 12a_1, the through hole 13a_1, and the through hole 13a_2 in the flow path cross section. It is penetratingly formed in a circular shape.

  The through hole 15a_1 of the fourth plate member 15 stacked on the first plate member 12_3 is formed at a position facing the center of the through hole 12a_3. The through hole 14a_1 of the third plate member 14 stacked on the fourth plate member 15 is formed at a position facing the through hole 15a_1.

  The through hole 15a_2 of the fourth plate member 15 stacked on the first plate member 12_3 is formed at a position facing the linear portion 112B of the through hole 12a_3. The through hole 14a_2 of the third plate member 14 stacked on the fourth plate member 15 is formed at a position facing the through hole 15a_2.

When the first plate member 12 to the fourth plate member 15 are stacked, the through holes formed in the first plate member 12 to the fourth plate member 15 communicate with each other, and the distribution flow channel 2a It is formed. That is, when the first plate member 12 to the fourth plate member 15 are stacked, the adjacent through holes communicate with each other, and a portion other than the communicating through holes is adjacent to each other. It is closed by the plate-like member 13, the third plate-like member 14, or the fourth plate-like member 15, and the distribution flow channel 2a is formed.
In the first distributor 2A, although the case where the distribution flow path 2a has four fluid outlets for one fluid inlet is illustrated as an example, the number of branches is limited to four. It is not something to do.

  As shown in FIGS. 11 and 13, the through hole 12a_4 formed in the first plate member 12_4, the through hole 13a_3 formed in the second plate member 13_3, and the through hole formed in the first plate member 12_3. 12a_3, a through hole 14a_2 formed in the third plate member 14, and a through hole 15a_2 formed in the fourth plate member 15 are formed in the facing direction of the through holes 14a_2 of the third plate member 14, The heat transfer tube 4 functions as a heat transfer tube insertion portion 2 b into which the tip end 4 a of the heat transfer tube 4 is inserted. That is, the through holes 12a_4, the through holes 13a_3, the through holes 12a_3, the through holes 14a_2, and the through holes 15a_2 are formed at positions opposed to the linear portion 112B positioned on the extension of the heat transfer tube 4. The heat transfer pipe 4 is connected to the first distributor 2 by inserting the heat transfer pipe 4 therein.

  Here, the tip end portion 4 a of the heat transfer tube 4 is located at an intermediate portion of the through hole 14 a _ 2 of the third plate member 14. That is, the tip end portion 4a of the heat transfer tube 4 is located at a position not in contact with the second plate-like member 13_2 and is located in the middle of the through hole 14a_2 of the third plate-like member 14 adjacent to the second plate-like member 13_2. There is. Therefore, the tip end 4a of the heat transfer tube 4 is located closer to the fluid inlet than the through hole 12a_3. The through hole 12a_3 functions as an intermediate portion 2c of the heat transfer tube insertion portion 2b.

<Flow of refrigerant in first distributor 2A>
The flow of the refrigerant in the first distributor 2A will be described below.
FIG. 14 is a development view of the first distributor 2A. FIG. 15 is a longitudinal sectional view of the first distributor 2A. In FIG. 15, for convenience of explanation, the thickness of the plate-like body is schematically illustrated as being uniform. Further, FIG. 15 shows a cross section cut along the fluid flow direction.

  As shown in FIGS. 14 and 15, the refrigerant flowing through the refrigerant pipe flows into the inside of the first distributor 2 with the through hole 12a_1 of the first plate member 12_1 as a fluid inlet. The refrigerant flowing from the through hole 12a_1 flows into the through hole 13a_1 of the second plate member 13_1.

  The refrigerant flowing from the through hole 12a_1 of the first plate member 12_1 into the through hole 13a_1 of the second plate member 13_1 flows into the center of the through hole 12a_2 of the first plate member 12_2. The refrigerant that has flowed into the center of the through hole 12a_2 of the first plate member 12_2 strikes the surface of the second plate member 13_2 stacked adjacent to it and branches off, and the end of the through hole 12a_2 of the first plate member 12_2 Flow. The refrigerant reaching the end of the through hole 12a_2 of the first plate member 12_2 passes through the through hole 13a_2 of the second plate member 13_2 and flows into the through hole 14a_1 of the third plate member 14.

  The refrigerant that has flowed into the through hole 14a_1 of the third plate member 14 flows into the through hole 15a_1 of the fourth plate member 15. The refrigerant that has flowed into the through hole 15a_1 of the fourth plate member 15 flows into the center of the through hole 12a_3 of the first plate member 12_3.

  The refrigerant that has flowed into the center of the through hole 12a_3 of the first plate member 12_3 strikes the surface of the second plate member 13_3 stacked adjacent to it and branches off, and the end of the through hole 12a_3 of the first plate member 12_3. Flow. The refrigerant reaching the linear portion 112B which is the end of the through hole 12a_3 of the first plate-like member 12_3 collides with the side surface of the heat transfer tube 4 passing through the through hole 12a_3. Since the through hole 12a_3 functions as the intermediate portion 2c of the heat transfer tube insertion part 2b, the refrigerant collides with the side surface of the heat transfer tube 4 at the through hole 12a_3 and then flows into the through hole 15a_2 of the fourth plate member 15 to pass through It flows toward the fluid inlet side than the hole 12a_3.

  The refrigerant flowing into the through hole 15 a 2 of the fourth plate member 15 flows into the through hole 14 a 2 of the third plate member 14. The through hole 14a_2 of the third plate member 14 functions as a fluid outlet, and the refrigerant reaching the through hole 14a_2 of the third plate member 14 is the tip 4a of the heat transfer tube 4 located in the through hole 14a_2. Flow into the inside of the heat transfer tube 4 from the

  The refrigerant that has flowed into the heat transfer tube 4 is inside the through hole 14a_2 of the third plate member 14, inside the through hole 15a_2 of the fourth plate member 15, inside of the through hole 12a_3 of the first plate member 12_3, second It passes through the inside of the through hole 13a_3 of the plate member 13_3 and the region located inside the through hole 12a_4 of the first plate member 12_4, and flows into the region of the heat transfer tube 4 to which the fins 5 are joined.

The refrigerant reaching the linear portion 112B, which is the end of the through hole 12a_3 of the first plate member 12_3, flows to the left and right in the drawing as shown in FIG.
In the case of the operation mode in which the heat exchanger 1 acts as an evaporator, the refrigerant reaching the linear portion 112B is in a gas-liquid two-phase state, and is scattered when it collides with the side surface of the heat transfer tube 4. By scattering the refrigerant, the gas phase and the liquid phase become homogeneous in the middle portion 2c of the heat transfer tube insertion portion 2b. The refrigerant flows into the heat transfer tube 4 in this homogeneous state.

  On the other hand, in the case of the operation mode in which the heat exchanger 1 acts as a condenser, the refrigerant flows from the through hole 14a_2 functioning as a fluid outlet into the inside of the first distributor 2A and flows through the distribution channel 2a, It flows out to the exterior of distribution channel 2a from penetration hole 12a_1 which functions as an entrance part. In the case of the operation mode in which the heat exchanger 1 functions as a condenser, the refrigerant flowing into the first distributor 2A is substantially in the liquid phase.

<Operation and Effect of First Distributor 2A, Heat Exchanger 1>
As described above, since the heat exchanger according to the second embodiment includes the first distributor 2A, in addition to the effects exhibited by the heat exchanger 1 according to the first embodiment, the heat transfer tube 4 is provided with gas and liquid Can flow in the refrigerant in a homogenized state, the liquid film on the inner wall surface of the heat transfer tube 4 becomes thin, and the heat transfer coefficient is improved. That is, according to the heat exchanger of the second embodiment, the heat exchanger performance is improved.

  Further, in the heat exchanger according to the second embodiment, when the heat transfer pipe 4 is a flat porous pipe, the refrigerant in a state in which gas and liquid are homogenized flows into each hole, so the heat exchange section is efficiently performed. The refrigerant can be evaporated. Therefore, according to the heat exchanger according to the second embodiment, the heat exchanger performance is improved, and high efficiency operation can be realized.

  Furthermore, in the operation mode in which the heat exchanger acts as a condenser, the actual volume in the heat transfer tube insertion portion 2b can be reduced by inserting the heat transfer tube 4 to the through hole 14a_2 of the third plate member 14, and the heat transfer tube The amount of stagnant refrigerant can be reduced at the insertion portion 2b. As a result, it is possible to realize a reduction in the amount of refrigerant enclosed as the entire refrigeration cycle apparatus, which is economical and effective for environmental protection at the time of refrigerant leakage.

The modification of the first embodiment shown in FIGS. 9 and 10 can also be applied as a modification of the second embodiment.
Further, the intermediate portion 2c does not mean a strictly intermediate portion of the heat transfer tube insertion portion 2b, and may be a portion where the side surface of the heat transfer tube 4 inserted in the heat transfer tube insertion portion 2b is located.

Third Embodiment
A refrigeration cycle apparatus according to Embodiment 3 of the present invention will be described.
<Configuration of Refrigeration Cycle Apparatus 100>
The schematic configuration of the refrigeration cycle apparatus 100 according to the third embodiment will be described below.
FIG. 16 is a circuit configuration diagram schematically showing an example of the refrigerant circuit configuration of the refrigeration cycle apparatus 100 according to the third embodiment. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as the first and second embodiments will be assigned the same reference numerals and descriptions thereof will be omitted. Further, in FIG. 16, the flow of the refrigerant during the cooling operation is indicated by a broken arrow, the flow of the refrigerant during the heating operation is indicated by a solid arrow, and the flow of the air is indicated by a white arrow.

  The refrigeration cycle apparatus 100 has a heat exchanger provided with the distributor according to the first or second embodiment as one of the configurations. For convenience of explanation, the refrigeration cycle apparatus 100 will be described as having the heat exchanger 1 provided with the first distributor 2 according to the first embodiment. In the third embodiment, the case where the refrigeration cycle apparatus 100 is an air conditioner will be described as an example.

  The refrigeration cycle apparatus 100 includes a first unit 100A and a second unit 100B as components. The first unit 100A is used as a heat source unit or an outdoor unit. The second unit 100B is used as an indoor unit or a use side unit (load side unit) or the like.

  In the first unit 100A, the compressor 101, the flow path switching device 102, the expansion device 104, the second heat exchanger 105, and the blower 105A attached to the second heat exchanger 105 are accommodated. The second heat exchanger 105 also includes the first distributor 2. That is, the second heat exchanger 105 is the one to which the heat exchanger 1 described in the first embodiment is applied.

  In the second unit 100B, a first heat exchanger 103 and a blower 103A attached to the first heat exchanger 103 are accommodated. In addition, the first heat exchanger 103 includes the first distributor 2. That is, the first heat exchanger 103 is the one to which the heat exchanger 1 described in the first embodiment is applied.

  And as shown in FIG. 16, the compressor 101, the 1st heat exchanger 103, the expansion device 104, and the 2nd heat exchanger 105 are connected by the refrigerant | coolant piping 106, and the refrigerant circuit is formed. The blower 103A is attached to the first heat exchanger 103, and supplies air to the first heat exchanger 103. The blower 105A is attached to the second heat exchanger 105 and supplies air to the second heat exchanger 105.

  The compressor 101 compresses a refrigerant. The refrigerant compressed by the compressor 101 is discharged and sent to the first heat exchanger 103 or the second heat exchanger 105. The compressor 101 can be configured by, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, and the like.

  The flow path switching device 102 switches the flow of the refrigerant in the heating operation and the cooling operation. That is, the flow path switching device 102 is switched to connect the compressor 101 and the first heat exchanger 103 during heating operation, and connects the compressor 101 and the second heat exchanger 105 during cooling operation. It is switched. The flow channel switching device 102 may be configured by, for example, a four-way valve. However, a combination of a two-way valve or a three-way valve may be employed as the flow path switching device 102.

  The first heat exchanger 103 functions as a condenser during heating operation and functions as an evaporator during cooling operation. That is, when functioning as a condenser, in the first heat exchanger 103, the high temperature / high pressure refrigerant discharged from the compressor 101 and the air supplied by the blower 103A exchange heat, and the high temperature / high pressure gas refrigerant condenses. . On the other hand, when functioning as an evaporator, in the first heat exchanger 103, the low-temperature low-pressure refrigerant flowing out from the expansion device 104 and the air supplied by the blower 103A exchange heat, and the low-temperature low-pressure liquid refrigerant or two-phase The refrigerant evaporates.

  The expansion device 104 expands and reduces the pressure of the refrigerant flowing out of the first heat exchanger 103 or the second heat exchanger 105. The expansion device 104 may be configured by, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant. As the expansion device 104, not only a motorized expansion valve but also a mechanical expansion valve employing a diaphragm in a pressure receiving portion, a capillary tube or the like can be applied.

  The second heat exchanger 105 functions as an evaporator during heating operation and functions as a condenser during cooling operation. That is, when functioning as an evaporator, in the second heat exchanger 105, the low-temperature low-pressure refrigerant flowing out of the expansion device 104 and the air supplied by the blower 105A exchange heat, and the low-temperature low-pressure liquid refrigerant or two-phase The refrigerant evaporates. On the other hand, when functioning as a condenser, in the second heat exchanger 105, the high temperature / high pressure refrigerant discharged from the compressor 101 and the air supplied by the blower 105A exchange heat, and the high temperature / high pressure gas refrigerant condenses. .

<Operation of Refrigeration Cycle Apparatus 100>
Next, the operation of the refrigeration cycle apparatus 100 will be described along with the flow of the refrigerant. Here, the operation of the refrigeration cycle apparatus 100 will be described by taking an example where the heat exchange fluid is air and the heat exchange fluid is a refrigerant.

  First, the cooling operation performed by the refrigeration cycle apparatus 100 will be described. In addition, the flow of the refrigerant | coolant at the time of cooling operation is shown by the broken line arrow of FIG.

  As shown in FIG. 16, by driving the compressor 101, the refrigerant in a high temperature / high pressure gas state is discharged from the compressor 101. Hereinafter, the refrigerant flows according to the broken arrow. The high temperature and high pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the second heat exchanger 105 functioning as a condenser via the flow path switching device 102. In the second heat exchanger 105, heat exchange is performed between the inflowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 105A, and the high-temperature and high-pressure gas refrigerant condenses to a high-pressure liquid refrigerant ( It becomes single phase).

  The high-pressure liquid refrigerant delivered from the second heat exchanger 105 is converted by the expansion device 104 into a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant. The two-phase refrigerant flows into the first heat exchanger 103 that functions as an evaporator. The first heat exchanger 103 includes the first distributor 2, and the refrigerant is distributed by the first distributor 2 according to the number of passes of the first heat exchanger 103 to form the first heat exchanger 103. Flows into the heat transfer tube 4.

  In the first heat exchanger 103, heat exchange is performed between the inflowing two-phase refrigerant and the air supplied by the blower 103A, and the liquid refrigerant in the two-phase refrigerant is evaporated to a low pressure. It becomes a gas refrigerant (single phase). The low-pressure gas refrigerant sent from the first heat exchanger 103 flows into the compressor 101 through the flow path switching device 102, is compressed, becomes a high-temperature and high-pressure gas refrigerant, and is discharged again from the compressor 101. Hereinafter, this cycle is repeated.

  Next, the heating operation performed by the refrigeration cycle apparatus 100 will be described. In addition, the flow of the refrigerant | coolant at the time of heating operation is shown by the continuous line arrow of FIG.

  As shown in FIG. 16, by driving the compressor 101, the refrigerant in a high temperature / high pressure gas state is discharged from the compressor 101. Hereinafter, the refrigerant flows according to the solid arrow. The high temperature and high pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the first heat exchanger 103 functioning as a condenser via the flow path switching device 102. In the first heat exchanger 103, heat exchange is performed between the inflowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 103A, and the high-temperature and high-pressure gas refrigerant condenses to a high-pressure liquid refrigerant ( It becomes single phase).

  The high-pressure liquid refrigerant delivered from the first heat exchanger 103 is converted by the expansion device 104 into a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant. The two-phase refrigerant flows into the second heat exchanger 105 which functions as an evaporator. The second heat exchanger 105 includes the first distributor 2, and the refrigerant is distributed by the first distributor 2 according to the number of paths of the second heat exchanger 105 to form the second heat exchanger 105. Flows into the heat transfer tube 4.

  In the second heat exchanger 105, heat exchange is carried out between the inflowing two-phase refrigerant and the air supplied by the blower 105A, and the liquid refrigerant in the two-phase refrigerant is evaporated to a low pressure. It becomes a gas refrigerant (single phase). The low-pressure gas refrigerant sent from the second heat exchanger 105 flows into the compressor 101 through the flow path switching device 102, is compressed, becomes a high-temperature and high-pressure gas refrigerant, and is discharged again from the compressor 101. Hereinafter, this cycle is repeated.

As described above, in the refrigeration cycle apparatus 100, the first distributor 2 is provided on the upstream side of the first heat exchanger 103 and the second heat exchanger 105.
Therefore, according to the refrigeration cycle apparatus 100, it is possible to realize the reduction of the cost required to manufacture the first heat exchanger 103 and the second heat exchanger 105, and the miniaturization and weight reduction of the heat exchanger 1.
In addition, if the refrigeration cycle apparatus 100 includes the first heat exchanger 103 and the second heat exchanger 105 including the first distributor 2A according to the second embodiment, the heat exchanger performance is further improved. .

  Here, the case where the heat exchanger according to the first embodiment or the heat exchanger according to the second embodiment is provided in both the first heat exchanger 103 and the second heat exchanger 105 has been described as an example. The heat exchanger according to the first embodiment or the heat exchanger according to the second embodiment may be provided in at least one of the first heat exchanger 103 and the second heat exchanger 105.

The refrigerant used in the refrigeration cycle apparatus 100 is not particularly limited, and the use of a refrigerant such as R410A, R32, or HFO 1234yf can exhibit the effect.
Also, although examples of air and refrigerant have been shown as the working fluid, the present invention is not limited to this, and the same effect can be obtained using other gas, liquid, and gas-liquid mixed fluid. In other words, the working fluid changes, and in any case, it works.
Furthermore, as another example of the refrigeration cycle apparatus 100, there are a water heater, a refrigerator, an air conditioning and hot water supply complex machine, etc. In any case, cost reduction, downsizing and weight reduction can be realized. If the distributor 2A is provided, it leads to further improvement of the heat exchanger performance.

  DESCRIPTION OF SYMBOLS 1 heat exchanger, 2 1st distributor, 2_1 mold, 2A 1st distributor, 2a distribution channel, 2a_1 wax pattern, 2b heat exchanger tube insertion part, 2c middle part, 3 2nd distributor, 3a joining channel , 4 heat transfer tube, 4a tip, 5 fins, 11 plate-like member, 12 first plate-like member, 12_1 first plate-like member, 12_2 first plate-like member, 12_3 first plate-like member, 12_4 first plate-like Members, 12a_1 through holes, 12a_2 through holes, 12a_3 through holes, 12a_4 through holes, 13 second plate members, 13_1 second plate members, 13_2 second plate members, 13_3 second plate members, 13a_1 through holes, 13a_2 through hole, 13a_3 through hole, 14 third plate member, 14a_1 through hole, 14a_2 through hole, 15 fourth plate member, 15a_1 through hole, 15a_2 through hole DESCRIPTION OF SYMBOLS 100 refrigeration cycle apparatus, 100A 1st unit, 100B 2nd unit, 101 compressor, 102 flow-path switching apparatus, 103 1st heat exchanger, 103A fan, 104 throttling apparatus, 105 2nd heat exchanger, 105A fan, 106 Refrigerant piping, 112A Z-shaped part, 112B straight part.

Claims (9)

A fluid inlet,
Multiple fluid outlets and
A distribution channel that communicates the fluid inlet with the plurality of fluid outlets, and distributes the fluid flowing in from the fluid inlet to the plurality of fluid outlets;
A plurality of heat transfer tube insertion parts formed in the facing direction of each of the plurality of fluid outlet parts and into which the heat transfer pipe is inserted;
The tip of the heat transfer tube inserted into the plurality of heat transfer tube insertion portions is connected to each of the plurality of fluid outlet portions. The plurality of fluid outlets are
The distributor according to claim 1, wherein the distributor is formed on an end side in the flow direction of the fluid in the distribution channel. The distribution channel is communicated with the middle part of the plurality of heat transfer tube insertion parts, and the fluid is made to collide with the side surface of the heat transfer tube inserted into the plurality of heat transfer pipe insertion parts, and then the fluid is introduced into the fluid inlet Configure to flow to the department side,
The plurality of fluid outlets are
The distributor according to claim 1, wherein the distributor is formed closer to the fluid inlet side than the plurality of heat transfer tube insertion parts. The opening area of the plurality of fluid outlet portions is
The distributor according to any one of claims 1 to 3, which is larger than the opening area of the end portion of the heat transfer tube. The fluid inlet portion, the distribution flow channel, the plurality of fluid outlet portions, and the plurality of heat transfer tube insertion portions
The distributor according to any one of claims 1 to 4, which is configured by laminating a plurality of plate-like bodies in which through holes are respectively formed. The distributor according to any one of claims 1 to 5,
And a plurality of heat transfer tubes into which the fluid flowing out from the plurality of fluid outlets of the distributor flows. In the one provided with the distributor according to claim 3,
The fluid that has reached the intermediate portion of the plurality of heat transfer tube insertion portions is
The heat exchanger according to claim 6, wherein the heat exchanger flows to the fluid inlet side by colliding with respective side surfaces of the plurality of heat transfer tubes inserted into the plurality of heat transfer tube insertion parts. The plurality of heat transfer tubes are circular tubes or flat tubes,
The heat exchanger according to claim 6 or 7. A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 6 to 7 as at least one of an evaporator and a condenser.

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